EP3225850A1 - Compresseur à spirales - Google Patents

Compresseur à spirales Download PDF

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Publication number
EP3225850A1
EP3225850A1 EP17163269.8A EP17163269A EP3225850A1 EP 3225850 A1 EP3225850 A1 EP 3225850A1 EP 17163269 A EP17163269 A EP 17163269A EP 3225850 A1 EP3225850 A1 EP 3225850A1
Authority
EP
European Patent Office
Prior art keywords
scroll
drive
oil
crankshaft
drive bush
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP17163269.8A
Other languages
German (de)
English (en)
Other versions
EP3225850B1 (fr
Inventor
Takuma YAMASHITA
Taichi Tateishi
Akihiro KANAI
Yoshiyuki Kimata
Hajime Sato
Yogo Takasu
Kazuki Takahashi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
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Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP3225850A1 publication Critical patent/EP3225850A1/fr
Application granted granted Critical
Publication of EP3225850B1 publication Critical patent/EP3225850B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/023—Lubricant distribution through a hollow driving shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/56—Bearing bushings or details thereof

Definitions

  • the present invention relates to a scroll compressor that improves the cooling capability of a drive bearing interposed together with a drive bush between a crankpin of a crankshaft for driving an Orbit Scroll and an Orbit boss part formed on a back surface of the Orbit Scroll.
  • a scroll compressor in which a drive bush is rotatably put in an Orbit boss part formed on a back surface of an end plate of an Orbit Scroll, a crankpin of a crankshaft is slidably fitted in a slide groove drilled on the drive bush, at least one or more through-holes along the axial direction are drilled on the above drive bush and further a radial-directional groove communicated with the through-holes is formed.
  • the position of the through-hole drilled on the drive bush is not necessarily optimized. That is, in the scroll compressor in which the crankshaft is disposed in the longitudinal direction, the lubricant oil is supplied through an oil supply passage formed along the shaft center line of the crankshaft, by an oil pump at a lower end of the crankshaft, and the lubricant oil is discharged from an upper end of the crankshaft and is refluxed to the oil pump side through interspaces of the drive bearing.
  • the amount of the lubricant oil to pass through the part of the drive bearing on which the load from the crankpin strongly acts is small in this way, it is hard to promote the thermal exhaust of the drive bearing, and the drive bearing sometimes causes the damage of the drive bearing such as early abrasion.
  • the suction amount of the lubricant oil by way of the crankshaft decreases. Therefore, an oil film is hard to form, and the problem becomes conspicuous.
  • the present invention has been made for solving the above problem, and has object to provide a scroll compressor that can improve the cooling capability of a drive bearing interposed together with a drive bush between a crankpin of a crankshaft for driving an Orbit Scroll and an Orbit boss part formed on a back surface of the Orbit Scroll.
  • the present invention employs the following solution.
  • a scroll compressor includes: a hermetic housing; a scroll compression mechanism in which a fixed scroll and an Orbit Scroll are combined, the scroll compression mechanism being installed at an upper site in the hermetic housing; an electric motor that is installed at a lower site of the scroll compression mechanism; a crankshaft that is rotationally driven by the electric motor; a crankpin that is provided at an upper end of the crankshaft and that is inserted into an Orbit boss part through a cylindrical drive bush and a drive bearing in a relatively rotatable manner, the Orbit boss part being formed on a back surface of the Orbit Scroll; an oil supply passage that is formed along a shaft center line of the crankshaft and through which lubricant oil is supplied to a vicinity of the drive bearing; and an oil through hole that has a through-hole shape and that is formed in an interior of a cylindrical wall of the drive bush along an axial direction, the oil through hole being formed in a predetermined load angle region in which an outer circumferential surface of the drive bush presses on an inner circum
  • the outer circumferential surface of the drive bush presses on the inner circumferential surface of the drive bearing, resulting in the generation of the predetermined load angle region in which the interspace between the outer circumferential surface of the crankpin and the inner circumferential surface of the drive bush and the interspace between the outer circumferential surface of the drive bush and the inner circumferential surface of the drive bearing decrease. Accordingly, the lubricant oil supplied to the vicinity of the drive bearing through the oil supply passage formed along the shaft center line of the crankshaft is difficult to reflux while passing through ranges of the interspaces that correspond to the load angle region, and the reflux amount of the lubricant oil in this region decreases.
  • the lubricant oil can be refluxed downward through the oil through hole that has a through-hole shape and that is formed in the drive bush so as to be adjacent to the load angle region. Therefore, the drive bush is cooled by the lubricant oil that passes through the oil through hole, and the thermal exhaust of the drive bearing adjacent to the drive bush is promoted. Accordingly, it is possible to prevent damage such as early abrasion at a part of the drive bearing that corresponds to the load angle region.
  • a plurality of the oil through holes be formed so as to be arrayed in a circumferential direction of the drive bush.
  • the scroll compressor according to the present invention it is possible to improve the cooling capability of the drive bearing interposed together with the drive bush between the crankpin of the crankshaft for driving the Orbit Scroll and the Orbit boss part formed on the back surface of the Orbit Scroll.
  • Fig. 1 is a vertical cross-sectional view of the whole of a scroll compressor according to an embodiment of the present invention.
  • a hermetic-type electric scroll compressor will be described as an example.
  • the present invention is not limited to this, and can be applied to an open type.
  • a scroll compressor 1 includes a cylindrical hermetic housing 2 that is vertically long, that has a bottom, and that is made of a steel plate.
  • a scroll compression mechanism 3 is installed at an upper site in the hermetic housing 2, and an electric motor 4 is installed at lower site therein.
  • the upper part side relative to the scroll compression mechanism 3 is a discharge chamber 5 that discharges the high-pressure gas compressed by the scroll compression mechanism 3, and is connected with a discharge pipe 6.
  • the lower part side relative to the scroll compression mechanism 3 is a suction chamber 7 that sucks low-pressure suction gas, and is connected with a suction pipe 8.
  • an electric motor 4 constituted by a stator 9 and a rotor 10 is installed in the hermetic housing 2 by press fitting or the like, and a crankshaft 11 that is linked with the rotor 10 of the electric motor 4 and that is rotationally driven by the electric motor 4 extends in the vertical direction.
  • a lower end part of the crankshaft 11 is supported by a lower part bearing 12 provided in the hermetic housing 2, and has a configuration in which a lubricant oil 14 stored in a bottom part of the hermetic housing 2 is supplied to main lubrication sites such as the scroll compression mechanism 3, an upper part bearing member 15 and a later-described drive bearing 26, through an oil supply passage 11a formed along the axial direction in the crankshaft 11, by a known oil supply pump 13 provided between the lower end part and the lower part bearing 12, and can lubricate those sites.
  • the oil supply passage 11a is opened at an upper part of the crankshaft 11.
  • the scroll compression mechanism 3 is installed in the hermetic housing 2 through the upper part bearing member 15.
  • the scroll compression mechanism 3 is constituted by a fixed scroll 16 that is fixedly installed on the upper part bearing member 15, and an Orbit Scroll 20 that is supported on the upper part bearing member 15 so as to be able to revolve and circulate around the fixed scroll 16.
  • the fixed scroll 16 includes a fixed end plate 17 and a fixed spiral lap 18 that stands on one surface of the fixed end plate 17, and has a configuration in which a discharge port 19 is provided at a center part of the fixed end plate 17.
  • the Orbit Scroll 20 includes a circulating end plate 21 and a circulating spiral lap 22 that stands on one surface of the circulating end plate 21, and has a configuration in which a cylindrical Orbit boss part 23 is integrally formed on the back surface side of the circulating end plate 21.
  • the fixed scroll 16 and the Orbit Scroll 20 are configured such that the fixed spiral lap 18 and the circulating spiral lap 22 are meshed by a known method while having a phase difference of 180 degrees and thereby a single compression space 24 is formed between both scrolls 16, 20.
  • the single compression space 24 is configured to be moved while the volume is decreased from an outer circumferential position to a center part by the revolution and circulation of the Orbit Scroll 20, and to exert a compression action.
  • the Orbit Scroll 20 has a configuration in which the back surface of the circulating end plate 21 is supported on a thrust bearing part 15A of the upper part bearing member 15, a crankpin 11A provided at an upper end of the crankshaft 11 is inserted into the Orbit boss part 23 on the back surface side through a drive bush 25 and a drive bearing 26 that constitute a known driven crank mechanism, in a relatively rotatable manner, and thereby, the revolution and circulation drive can be performed around the fixed scroll 16 such that the circulating radius can be changed.
  • Reference character 25W denotes a balancer weight that is provided integrally with the drive bush 25.
  • a rotation prevention means 27 including an Oldham ring and the like and blocking the rotation of the Orbit Scroll 20 is incorporated between the back surface of the circulating end plate 21 of the Orbit Scroll 20 and the thrust bearing part 15A of the upper part bearing member 15.
  • the upper part of the crankshaft 11 is rotatably supported by a journal bearing part 15B of the upper part bearing member 15.
  • a discharge cover 28 is provided on the back surface side, and a reed-valve-type discharge valve 29 for opening and closing the discharge port 19 is provided.
  • a plurality of relief ports 30 having a plurality of holes for communicating between the compression space 24 and the discharge chamber 5, and a relief valve 31 for opening and closing the port 30 are provided at a plurality of positions with different circulating angles along the spiral direction of the fixed spiral lap 18 on the outer circumference side of the discharge port 19 provided at the center part.
  • the lubricant oil 14 to be supplied to the scroll compression mechanism 3 and the like through the oil supply passage 11a formed in the crankshaft 11 is supplied to the drive bush 25, the drive bearing 26, the thrust bearing part 15A and the like.
  • the drive bearing 26 not a rolling bearing but a sliding bearing is selected because of the supply capability of the lubricant oil 14 and the space relation.
  • Fig. 2 is an enlarged vertical cross-sectional view of the drive bush 25, and Fig. 3 is a plan view of the drive bush 25, viewed along arrow III in Fig. 2 .
  • a plurality of oil through holes 25a having a through-hole shape along the axial direction are formed in the interior of the cylindrical wall of the cylindrically formed drive bush 25.
  • the oil through holes 25a for example, three round holes are formed.
  • the hole shape and the number are not limited to this, and it is possible that the hole shape is another shape or the number is one or four or more.
  • the oil through hole 25a may be a curved elongate hole that extends in the circumferential direction of the drive bush 25, if the strength of the drive bush 25 is satisfied.
  • the oil through holes 25a are formed in accordance with a predetermined load angle region ⁇ in which the outer circumferential surface of the drive bush 25 to be pushed outward in the radial direction by the pressure from the crankpin 11A of the crankshaft 11 presses on the inner circumferential surface of the drive bearing 26 at the time of the load operation of the scroll compressor 1.
  • the angle of the load angle region ⁇ is about 60 degrees to 80 degrees.
  • the oil through holes 25a may be formed over a somewhat wider range.
  • crankpin 11A is slightly decentered with respect to the inner circumferential surface of the drive bush 25, and an interspace S1 between the outer circumferential surface of the crankpin 11A and the inner circumferential surface of the drive bush 25 increases in a region opposite to the load angle region ⁇ .
  • an interspace S2 between the outer circumferential surface of the drive bush 25 and the inner circumferential surface of the drive bearing 26 increases. It is desirable that the oil through holes 25a be at an about 180-degree opposite side to positions of the interspaces S1, S2 where the widths are maximized.
  • the outer circumferential surface of the crankpin 11A presses on the inner circumferential surface of the drive bush 25, and the outer circumferential surface of the drive bush 25 presses on the inner circumferential surface of the drive bearing 26, resulting in the generation of the predetermined load angle region ⁇ in which the interspace S1 between the outer circumferential surface of the crankpin 11A and the inner circumferential surface of the drive bush 25 and the interspace S2 between the outer circumferential surface of the drive bush 25 and the inner circumferential surface of the drive bearing 26 decrease.
  • the lubricant oil 14 supplied to the vicinity of the drive bearing 26 through the oil supply passage 11a formed along the shaft center line of the crankshaft 11 is difficult to reflux while passing through ranges of the interspaces S1, S2 that correspond to the load angle region ⁇ , and the reflux amount of the lubricant oil 14 in this region decreases.
  • the lubricant oil 14 can be refluxed downward through the three oil through holes 25a that have a through-hole shape and that are formed in the drive bush 25 so as to be adjacent to the load angle region ⁇ . Therefore, the drive bush 25 is cooled by the lubricant oil 14 that passes through the oil through holes 25a, and the thermal exhaust of the drive bearing 26 adjacent to the drive bush 25 is promoted. Accordingly, it is possible to prevent damage such as early abrasion at a part of the drive bearing 26 that corresponds to the load angle region ⁇ . This is particularly effective in the case where the drive bearing 26 is a sliding bearing as shown in the embodiment. Meanwhile, on the non-load side, the interspaces S1, S2 are enlarged, and therefore, also from these, a lot of the lubricant oil 14 is refluxed. Therefore, the whole circumference of the drive bush 25 is cooled.
  • the plurality of the oil through holes 25a are formed so as to be arrayed in the circumferential direction of the drive bush 25, and therefore, it is possible to make the oil through holes 25a exist over the whole range of the load angle region ⁇ extending in the circumferential direction of the drive bush 25, and to enhance the cooling effect of the drive bush 25. Furthermore, it is possible to reduce the inner diameter of each oil through hole 25a, and therefore, it is possible to avoid the decrease in the strength of the drive bush 25 due to the drilling of the oil through holes 25a.
  • the scroll compressor 1 it is possible to improve the cooling capability of the drive bearing 26 interposed together with the drive bush 25 between the crankpin 11A of the crankshaft 11 for driving the Orbit Scroll 20 and the Orbit boss part 23 formed on the back surface of the Orbit Scroll 20, and it is possible to avoid the damage of the drive bearing 26.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP17163269.8A 2016-03-31 2017-03-28 Compresseur à spirales Active EP3225850B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2016071994A JP6771928B2 (ja) 2016-03-31 2016-03-31 スクロール圧縮機

Publications (2)

Publication Number Publication Date
EP3225850A1 true EP3225850A1 (fr) 2017-10-04
EP3225850B1 EP3225850B1 (fr) 2018-12-26

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ID=58448439

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17163269.8A Active EP3225850B1 (fr) 2016-03-31 2017-03-28 Compresseur à spirales

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EP (1) EP3225850B1 (fr)
JP (1) JP6771928B2 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03105093A (ja) * 1989-09-18 1991-05-01 Daikin Ind Ltd スクロール形流体機械
JPH0449684U (fr) 1990-08-30 1992-04-27
US5542830A (en) * 1994-08-09 1996-08-06 Mitsubishi Jukogyo Kabushiki Kaisha Bearing lubrication for scroll-type compressor
WO2015049745A1 (fr) * 2013-10-02 2015-04-09 三菱電機株式会社 Compresseur à spirale

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03105093A (ja) * 1989-09-18 1991-05-01 Daikin Ind Ltd スクロール形流体機械
JPH0449684U (fr) 1990-08-30 1992-04-27
US5542830A (en) * 1994-08-09 1996-08-06 Mitsubishi Jukogyo Kabushiki Kaisha Bearing lubrication for scroll-type compressor
WO2015049745A1 (fr) * 2013-10-02 2015-04-09 三菱電機株式会社 Compresseur à spirale

Also Published As

Publication number Publication date
EP3225850B1 (fr) 2018-12-26
JP6771928B2 (ja) 2020-10-21
JP2017180407A (ja) 2017-10-05

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